EP2737177A1 - Rotary piston engine - Google Patents

Rotary piston engine

Info

Publication number
EP2737177A1
EP2737177A1 EP12817318.4A EP12817318A EP2737177A1 EP 2737177 A1 EP2737177 A1 EP 2737177A1 EP 12817318 A EP12817318 A EP 12817318A EP 2737177 A1 EP2737177 A1 EP 2737177A1
Authority
EP
European Patent Office
Prior art keywords
piston
shaft
rotation
centre
path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12817318.4A
Other languages
German (de)
French (fr)
Other versions
EP2737177A4 (en
Inventor
Risto Auvinen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Steammotor Finland Ltd Oy AB
Original Assignee
Steammotor Finland Ltd Oy AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Steammotor Finland Ltd Oy AB filed Critical Steammotor Finland Ltd Oy AB
Publication of EP2737177A1 publication Critical patent/EP2737177A1/en
Publication of EP2737177A4 publication Critical patent/EP2737177A4/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft

Definitions

  • This invention relates to a rotary piston engine according to the preamble of claim 1.
  • Such a rotary piston machine in which a centre shaft of a moving piston is the rotation axis of piston rotation and in which a rotational motion of the piston is arranged to rotate around a rotation support shaft moving around a centre point of a motion space of the piston, is previously known from specification US5431551.
  • the rotation support shaft of the moving piston of this machine moves continuously rolling along a specific path such that the difference between a torque arm length and a lever arm length of a torque structure of the piston varies, whereby the production of mechanical energy is irregular and weak at the point of some piston positions.
  • Power transmission is connected via an eccentric shaft solely to motions rotating around the rotation support of the piston and this machine does not include power transmission comprising kinetic energy transmission of the spinning motion of the piston around its centre shaft.
  • Such a device in which striking motions of the piston are arranged to rotate such that the rotation support shaft in one of stationary rotation support points being at an equal distance from the centre point of the motion space, is previously known from published application WO2010/026288.
  • a piston rotation cycle is formed of eight successive striking motion sections around polar axes being alternately in two rotation support points such that, in a path of piston angles, there are sections identical in relation to each other only in twos, and two bends in a path of a centre shaft of the moving piston are on the symmetry axis of the path, whereby bends on the path of the centre shaft and the path of the piston angles are sharp and torque transmitting to the main shaft becomes strongly pulsating, which causes energy losses and difficult-to-control inertia forces stressing the piston and the power transmission device.
  • Transmission of kinetic energy in this machine connecting spinning motions of the piston around its centre shaft and spinning motions of the main shaft is arranged by a power transmission device comprising a crank device, a pivoted beam and a flywheel, but transmission of kinetic energy between the striking motions of the piston rotating around two rotation support points and the spinning motion of the main shaft is not technically directly arrangeable due to the oval shape and the sharp bends of the path of the centre shaft of the piston.
  • the object of the invention is to eliminate above disadvantages, to improve the total efficiency of a rotary piston engine and to provide a rotary piston engine the path of the centre shaft of the moving piston of which is formed such that the rotations of the centre shaft and the piston angles are controlled along their own gentle-bended paths, the rotation volume is large and the striking motions of the piston have effective torque.
  • a further object is to provide a rotary piston engine between the piston and the main shaft of which there are two moment lines technically available for transmitting kinetic energy, which are arranged both from the rotational motions of the piston around the rotation support and from the spinning motions of the piston around its centre shaft.
  • the 360-degree rotation of the angles of the moving piston of the rotary piston engine is formed from at least twelve successive striking motion sections which are arranged to rotate for the duration of the striking motion around a polar axis being in one of at least three different rotation support points such that torque in the piston rotation around its centre shaft is even and to the path of the piston angles are formed at least three sections identical in relation to each other and the motions of the centre shaft of the piston are on a planetary path which includes substantially the same number of sections and bends, at the point of which rotations are gentle, for the rotation support points such that inertia forces caused by the motions of the piston are controlled and that from the rotational motions of the piston around the rotation support points and from the spinning motions of the piston around its centre shaft are arranged two connectable moment lines suitable for transmitting kinetic energy between the piston and the main shaft.
  • the number of rotation support points is divisible by three and walls of the motion space of the piston are formed by three sections identical in relation to each other, whereby bends on both the path of the piston angles and the planetary path of the centre shaft of the piston are gentle, which has decreased kinetic friction and increased the output of the rotary piston engine through two kinetic-energy moment lines.
  • the extreme end of the torque structure of the moving piston of the rotary piston engine is at a distance of a relatively long, standard-length radius from the rotation support point of the striking motion of the piston, which has provided the large rotation volume of the rotation space of the rotary piston engine and the large; standard-length lever arm length of the torque structure of the piston.
  • angular speed of the extreme end of the torque structure of the piston is constant, which has increased the even and effective torque.
  • transmission of kinetic energy with drive wheels is arranged by connecting a drive wheel to the piston substantially at the point of the rotation axis of the piston and by connecting a second drive wheel to the main shaft substantially aligned to the centre point of the motion space of the piston such that the drive wheels form a wheel pair through which the efficiency of the rotary piston engine is improved by connecting the moment lines from both the rotational motions and the spinning motions of the piston and a light-frictioned power transmission solution transmitting the output of the rotary piston engine in its entirety is provided.
  • the drive wheels are a wheel pair such that the rotational speed of the main shaft provided by their gear ratio is about 1.7 times higher than the rotational speed of the piston, thus providing even by a moderate rotational speed of the piston sufficient rotational speed of the main shaft for the effective use of an electric generator.
  • Fig. 1 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a rotation support point and of its rotation around a centre shaft being the rotation axis,
  • Fig. 2 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a second rotation support point and of its rotation around a centre shaft being the rotation axis
  • Fig. 3 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a third rotation support point and of its rotation around a centre shaft being the rotation axis
  • Fig. 3 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a third rotation support point and of its rotation around a centre shaft being the rotation axis
  • FIG. 4 shows an application of arranging in coordinates rotation support points of striking motions of a piston of a rotary piston engine according to the invention, of determining the shape of sections on a wall frame of a rotation space of the piston as well as the shape of a path of the wall frame and piston angles and the shape of a path of a centre shaft of the piston on circular arches the rotation support points being the centre point of the striking motions, and of positioning flow openings and grooves of medium,
  • Fig. 5 shows an application of a drive wheel belonging to a wheel pair of a power transmission device of a rotary piston engine according to the invention connected to a centre shaft of the rotary piston and of a second drive wheel connected to a main shaft and of alignment marks which are at the point of each other in the drive wheels in the situation of the figure,
  • Fig. 6 shows an application of a drive wheel belonging to a wheel pair of a power transmission device of a rotary piston engine according to the invention connected to a centre shaft of the rotary piston and of a second drive wheel connected to the main shaft, and
  • Fig. 7 shows cross-sections of an application of a rotary piston engine according to the invention, of a power transmission device with its drive wheels, a main shaft, a mounting support, bearings and a base.
  • the figures show a piston 1, a wall frame 2 of a rotation space, a drive wheel 3 connected to the piston, a main shaft 4, a drive wheel 5 connected to the main shaft, a mounting support 6, a base 7, bearings 8, a cylinder block 9, covers 10, an inlet opening 11 of medium, flow grooves 12 of medium, an outlet opening 13 of medium, and outlet grooves 14 of medium.
  • a path of each piston angle is according to one of wall sections being in the wall frame 2 of rotation spaces shown in the figures and a section of a path of the centre shaft K of the piston is formed around the same rotation support point as the path of the piston angles.
  • the rotation support points are eccentrically at a distance from a centre point of the rotation space of the piston such that an extreme end of a torque structure of the piston is at an extreme end of an eccentric structure of the piston at a distance of a relatively long, standard-length radius from the rotation support point of the striking motion.
  • the paths of piston angles and the section of the path of the centre shaft K of the moving piston are formed around a common rotation support point of circular-arch shape such that, on the centre shaft K of the piston, there is a planetary shaft rotating on a path of regular shape, which is the rotation axis of the piston.
  • Transmission of kinetic energy between the piston 1 and the main shaft 4 is arranged connectedly by a wheel pair, the drive wheel 3 belonging to it is connected at the point of the centre shaft K of the piston such that it moves according to the rotational motions of the piston moving on a path surrounding the centre point of the motion space of the piston rotating around rotation supports and at the same time spinning according to the spinning motions of the centre shaft of the piston, and the drive wheel 5 is connected to the main shaft 4 aligned to a centre point O of the motion space of the piston such that the drive wheels collecting the kinetic energy of two moment lines are within each other as a wheel pair and, by the gear ratio of the wheel pair, the rotational speed of the main shaft is about 1.72 times higher that the rotational speed of the piston.
  • Controls of the motions of the piston 1 are wall sections of the wall frame 2 of the rotation space along which the piston angles glide, bearings in the centre shaft and bearings in the main shaft 4. In the piston angles, there can be a roll and sealing material to decrease friction.
  • the rotation cycle of the angles of the piston 1 is formed of twelve successive striking motion sections the polar axis being during one striking motion in one of three rotation support points P, PI or P2, which are at an equal distance from the centre point of the motion space.
  • the extreme end of the torque structure of the moving piston 1 is at the extreme end of the eccentric structure of the piston at a distance of a relatively long, standard-length radius a from the support point P, PI or P2 of rotational motion such that the path of the piston angles is formed by three sections identical in relation to each other.
  • the centre shaft K of the piston is always at a distance of a standard-length radius b from the same support point of rotational motion as the extreme end of the eccentric structure of the piston, and of sections A-B, B-C and C-A of the path of the centre shaft of the piston is formed a planetary path on the sections of which the angular speed of the centre shaft K of the rotating piston is constant.
  • the inlet opening 11 of medium and filling chambers are designated with an open arrow and the outlet opening 13 and emptying chambers with a solid arrow. According to Fig.
  • the rotation cycle of the angles of the piston 1 is formed of sixteen successive striking motion sections the polar axis being in one of four rotation support points P, PI, P2 or P3, which are at an equal distance from the centre point O of the motion space such that the path includes four sections identical in relation to each other.
  • the path of the piston angles follows the wall sections of the wall frame 2 of the rotation space and each position of the piston controls pressure and underpressure via valve openings and grooves in the chambers of the rotation space such that the medium fills the chambers expanding of their volume and the chambers contracting of their volume are emptied.
  • the extreme end of the torque structure of the moving piston 1 is at the extreme end of the eccentric structure of the piston, which is at a distance of a relatively long, standard-length radius a from the support point P, PI, P2 or P3 of rotational motion.
  • the centre shaft K of the piston is always at a distance of a standard-length radius b from the same rotation support point as the extreme end of the eccentric structure of the piston, and of sections A-B, B-C, C-D and D-A of the path of the centre shaft K of the piston is formed a planetary path at a distance from the centre point O of the rotation space, on the sections of which the angular speed of the centre shaft K of the rotating piston is constant.
  • the wheel pair 3, 5 of the power transmission device of the rotary piston engine is in connection with the piston such that the drive wheel 3 is connected at the point of the centre shaft K of the piston and the drive wheel 5 is connected to the main shaft 4 aligned to the centre point O of the motion space of the piston.
  • the piston 1 moving in the motion space 2 spins around its centre shaft K and at the same time the centre shaft of the piston rotates around the centre point O of the motion space following a path k.
  • the continuous contact of the drive wheels being within each other is arranged such that the difference between the length of reference diameters of the drive wheels is the length of the greatest diameter d of the path, and the length 2 x d of a reference diameter of the drive wheel is substantially two thirds of the length of a reference diameter h of the second drive wheel.
  • the main shaft 4 of the rotary piston engine is aligned by the mounting support 6 to the centre point O of the motion space of the piston such that a wheel pair has been formed of the drive wheels 3, 5 and the cylinder block 9 and the mounting support 6 are mountedly on the base 7.
  • the figure system comprising a section limited by twelve 30-degree curved lines showing the cross-section of the path of the angles of the quadratic piston and the wall frame of the rotation space and a section showing three 30-degree sections on the circular-arch shaped path of the centre shaft of the piston is formed in the following way:
  • the points P, PI and P2 being the rotation support points of the striking motions of the piston are the vertex in an isosceles triangle the side length of which is the difference between the length of the hypotenuse and the length of the side of the quadratic piston.
  • the piston is illustrated with a lever arm a, the length of which is 0.7 parts of the length of the hypotenuse of the quadratic piston, and the outer end of which is at the extreme end of the torque structure of the piston the inner end being the polar axis in the rotation support point P, PI or P2.
  • the distance of the centre shaft K of the piston to the rotation support point is a radius designated by a segment b the length of which is 0.2828 parts of the length of the piston side.
  • the polar axis being at the inner end of the torque arm operating in the next stroke sets to its rotation support point.
  • the piston angles are moved along the wall sections of the wall frame 2 of the rotation space and the centre shaft K of the piston is moved along the planetary path which includes bends A, B and C and sections A-B, B-C and C-A.
  • the figure system comprising a section limited by sixteen 22.5 -degree curved lines showing the cross-section of the path of the angles of the quadratic piston and the wall frame of the rotation space and a section showing four 22.5-degree sections on the circular-arch shaped path of the centre shaft of the piston is formed in the following way using coordinates:
  • the piston angles are moved along the wall sections of the wall frame 2 of the rotation space and the centre shaft K of the piston is moved along the planetary path, the bends A, B, C and D of which are at the point of the x axis and the y axis as the vertex in a quadratic figure, the length of the hypotenuse of which is 0.1718 parts of the length of the side of the quadratic piston and the centre point of which is at the point of the centre point O of the rotation space.
  • the points P, PI, P2 and P3 being the rotation support points of the striking motions of the piston are the vertex in a square symmetrical in relation to the x axis and the y axis the length of the side of which is 0.33 parts of the length of the piston side.
  • the piston is illustrated with a lever arm a, the length of which is 0.7 parts of the length of the hypotenuse of the quadratic piston, and the outer end of the lever arm a is at the extreme end of the torque structure of the piston the inner end being the polar axis in the rotation support point P, PI, P2 or P3.
  • the distance of the centre shaft K of the piston to the rotation support point is a radius designated by a segment b the length of which is 0.2828 parts of the length of the piston side.
  • the drive wheel 3 provided with an inner cogged ring belonging to the power transmission device of the rotary piston engine according to the application of Figs. 5 and 6 is connected at the point of the centre shaft K of the piston such that it moves according to the rotational motions of the centre shaft of the moving piston by rotating and at the same time according to the spinning motions of the centre shaft of the piston by spinning.
  • the drive wheel 5 cogged of its outer race is connected to the main shaft 4 aligned to the centre point O of the motion space of the piston such that the drive wheels are within each other.
  • a reference diameter of the drive wheel 5 is substantially two times longer than the greatest diameter d of the path k of the centre shaft of the piston and two thirds of the length of a reference diameter h of the drive wheel 3, whereby the drive wheels 3 and 5 form a wheel pair which has simultaneously provided the transmission of kinetic energy between both the rotational motions of the centre shaft of the piston and the spinning motions of the centre shaft and the spinning motions of the main shaft such that for one piston round the main shaft spins for about 620 degrees.
  • Alignment marks L and M illustrate in Fig. 6 that the drive wheel 3 connected to the piston has rotated according to the alignment mark L starting from the situation of Fig. 5 for a 45-degree stroke spinning around the centre shaft such that the drive wheel 5 connected to the main shaft has rotated starting from the situation of Fig. 1 for about 77 degrees, as the alignment mark M shows.
  • the rotation support points of the rotary piston engine according to the invention implement the striking motions of the piston such that, on the path of the piston angles, there are at least three sections identical in relation to each other, and the even, continuous rotation of the centre shaft K of the piston is formed by a closed planetary path at the point of bends of which the rotations are gentle.
  • the rotational speed of the centre shaft on the different sections of the planetary path is constant and each section equals the number of degrees of the striking section of the torque structure of the piston.
  • the planetary path substantially includes as many bends as there are rotation support points.
  • the striking motions of the piston and the sections of the paths of the centre shaft K of the piston are controlled in relation to each other in the rotation support points such that they have a common rotation support point, their striking sections are simultaneous and they include the same number of degrees.
  • the length of the lever arm a is the distance between the rotation support point and the extreme end of the torque structure of the piston, the angle being the extreme end of the torque structure is of the piston angles at the greatest distance from the rotation support point and the sections identical in relation to each other E-F, G-H and I-J of the path of the extreme end shown in Figs. 1-3, and the sections identical in relation to each other E-F, G-H, H-I and J-Kl of the path of the extreme end shown in Fig. 4 are the longest wall sections of the wall frame of the rotation space, and the angular speed of the piston angle moving at their point is constant when moving the piston at an even rotational speed.
  • the 360-degree rotation of the angles of the moving piston is formed from at least twelve successive striking motion sections of circular- arch shape which are arranged to rotate for the duration of the striking motion around a polar axis being in one of at least three different rotation support points such that torque in the piston rotation around its centre shaft is even and to the path of the piston angles is formed at least three sections identical in relation to each other and the motions of the centre shaft K of the piston are on a planetary path which includes substantially the same number of sections and bends, at the point of which rotations are gentle, for the rotation support points such that inertia forces caused by the motions of the piston are controlled.
  • the piston 1 When the piston 1 is moved by the pressure effect of a medium, e.g. vapour, or by kinetic energy obtained from the main shaft 4, the medium is conveyed to chambers expanding of their volume of the rotation space of the piston through the inlet opening and grooves shown in Fig. 4. Due to a groove, an opening is formed in the wall of the rotation space from which the medium flows around the corner. From the chambers contracting of their volume, the medium exits through the outlet opening and grooves shown in Fig. 4. It is natural that, in the different applications of the invention, the rotational motions and rotation of the piston can be switched to the right or the left or into both directions, e.g. the size and shape of the openings and grooves can be different from the application of Fig. 4 and e.g. the piston walls can include recesses and projections of different shapes.
  • a medium e.g. vapour
  • the piston walls can include recesses and projections of different shapes.
  • the rotation space of the piston of the rotary piston engine can be formed for a triangular or e.g. hexagonal rotary piston.
  • the drive wheel belonging to the power transmission device of the rotary piston engine is connected to a crank device mounted as an extension of the centre shaft of the piston such that it moves rotating according to the rotational motions of the piston and at the same time spinning according to the spinning motions of the centre shaft of the piston, and the second drive wheel belonging to the power transmission device is connected to the main shaft aligned to the centre of the motion space of the piston such that the drive wheels form a wheel pair connecting the crank device and the main shaft.
  • the power transmission between the piston and the main shaft of the rotary piston engine is arranged by an intermediate shaft which is not parallel with the centre shaft of the piston and which is between the piston and the main shaft pivotedly mounted from its both ends.
  • operating pressure of the rotary piston engine is arranged produceable in the motion space of the piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)

Abstract

The invention relates to a rotary piston engine which includes a piston (1), a motion space of the piston in which striking motions of the piston (1) are arranged to rotate such that a rotation support shaft is in one of stationary rotation support points being at an equal distance from a centre point of the motion space, and as a path of a centre shaft of the piston is formed a planetary path such that, at the point of the centre shaft of the piston (1) or in its immediate vicinity, there is a planetary shaft being the rotation axis of the rotation of the piston (1), and a power transmission device. In the rotary piston engine according to the invention, the 360-degree rotation of the angles of the moving piston (1) is formed from at least twelve successive striking motion sections which are arranged to rotate for the duration of the striking motion around a polar axis being in one of at least three different rotation support points (P, PI or P2) such that torque in the piston rotation around its centre shaft (K) is even and to the path of the piston angles are formed at least three sections identical in relation to each other and motions of the centre shaft (K) of the piston are on a planetary path which includes substantially the same number of sections (A-B, B-C, C-A) and bends (A, B, C), at the point of which rotations are gentle, such that inertia forces caused by the motions of the piston are controlled, and that of rotational motions of the piston around the rotation support points (P, PI or P2) and spinning motions around its centre shaft (K) are arranged two connectable moment lines between the piston (1) and the main shaft (4) suitable for transmitting kinetic energy.

Description

ROTARY PISTON ENGINE
This invention relates to a rotary piston engine according to the preamble of claim 1.
Such a rotary piston machine, in which a centre shaft of a moving piston is the rotation axis of piston rotation and in which a rotational motion of the piston is arranged to rotate around a rotation support shaft moving around a centre point of a motion space of the piston, is previously known from specification US5431551. The rotation support shaft of the moving piston of this machine moves continuously rolling along a specific path such that the difference between a torque arm length and a lever arm length of a torque structure of the piston varies, whereby the production of mechanical energy is irregular and weak at the point of some piston positions. Power transmission is connected via an eccentric shaft solely to motions rotating around the rotation support of the piston and this machine does not include power transmission comprising kinetic energy transmission of the spinning motion of the piston around its centre shaft.
Such a device, in which striking motions of the piston are arranged to rotate such that the rotation support shaft in one of stationary rotation support points being at an equal distance from the centre point of the motion space, is previously known from published application WO2010/026288. In this machine, a piston rotation cycle is formed of eight successive striking motion sections around polar axes being alternately in two rotation support points such that, in a path of piston angles, there are sections identical in relation to each other only in twos, and two bends in a path of a centre shaft of the moving piston are on the symmetry axis of the path, whereby bends on the path of the centre shaft and the path of the piston angles are sharp and torque transmitting to the main shaft becomes strongly pulsating, which causes energy losses and difficult-to-control inertia forces stressing the piston and the power transmission device. Transmission of kinetic energy in this machine connecting spinning motions of the piston around its centre shaft and spinning motions of the main shaft is arranged by a power transmission device comprising a crank device, a pivoted beam and a flywheel, but transmission of kinetic energy between the striking motions of the piston rotating around two rotation support points and the spinning motion of the main shaft is not technically directly arrangeable due to the oval shape and the sharp bends of the path of the centre shaft of the piston. The object of the invention is to eliminate above disadvantages, to improve the total efficiency of a rotary piston engine and to provide a rotary piston engine the path of the centre shaft of the moving piston of which is formed such that the rotations of the centre shaft and the piston angles are controlled along their own gentle-bended paths, the rotation volume is large and the striking motions of the piston have effective torque. A further object is to provide a rotary piston engine between the piston and the main shaft of which there are two moment lines technically available for transmitting kinetic energy, which are arranged both from the rotational motions of the piston around the rotation support and from the spinning motions of the piston around its centre shaft.
This object is provided by a rotary piston engine according to the invention which is characterised by what is presented in the characterising part of claim 1.
According to the invention, the 360-degree rotation of the angles of the moving piston of the rotary piston engine is formed from at least twelve successive striking motion sections which are arranged to rotate for the duration of the striking motion around a polar axis being in one of at least three different rotation support points such that torque in the piston rotation around its centre shaft is even and to the path of the piston angles are formed at least three sections identical in relation to each other and the motions of the centre shaft of the piston are on a planetary path which includes substantially the same number of sections and bends, at the point of which rotations are gentle, for the rotation support points such that inertia forces caused by the motions of the piston are controlled and that from the rotational motions of the piston around the rotation support points and from the spinning motions of the piston around its centre shaft are arranged two connectable moment lines suitable for transmitting kinetic energy between the piston and the main shaft.
In an advantageous application of the invention, the number of rotation support points is divisible by three and walls of the motion space of the piston are formed by three sections identical in relation to each other, whereby bends on both the path of the piston angles and the planetary path of the centre shaft of the piston are gentle, which has decreased kinetic friction and increased the output of the rotary piston engine through two kinetic-energy moment lines.
In a second application of the invention, the extreme end of the torque structure of the moving piston of the rotary piston engine is at a distance of a relatively long, standard-length radius from the rotation support point of the striking motion of the piston, which has provided the large rotation volume of the rotation space of the rotary piston engine and the large; standard-length lever arm length of the torque structure of the piston.
In a third application of the invention, angular speed of the extreme end of the torque structure of the piston is constant, which has increased the even and effective torque.
In a fourth application of the invention, between the piston and the main shaft of the rotary piston engine, transmission of kinetic energy with drive wheels is arranged by connecting a drive wheel to the piston substantially at the point of the rotation axis of the piston and by connecting a second drive wheel to the main shaft substantially aligned to the centre point of the motion space of the piston such that the drive wheels form a wheel pair through which the efficiency of the rotary piston engine is improved by connecting the moment lines from both the rotational motions and the spinning motions of the piston and a light-frictioned power transmission solution transmitting the output of the rotary piston engine in its entirety is provided. The drive wheels are a wheel pair such that the rotational speed of the main shaft provided by their gear ratio is about 1.7 times higher than the rotational speed of the piston, thus providing even by a moderate rotational speed of the piston sufficient rotational speed of the main shaft for the effective use of an electric generator. The invention will now be described in more detail with reference to the accompanying drawings in which
Fig. 1 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a rotation support point and of its rotation around a centre shaft being the rotation axis,
Fig. 2 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a second rotation support point and of its rotation around a centre shaft being the rotation axis, Fig. 3 shows an application of a stroke of a piston of a rotary piston engine according to the invention moving in a rotation space around a polar axis being in a third rotation support point and of its rotation around a centre shaft being the rotation axis, Fig. 4 shows an application of arranging in coordinates rotation support points of striking motions of a piston of a rotary piston engine according to the invention, of determining the shape of sections on a wall frame of a rotation space of the piston as well as the shape of a path of the wall frame and piston angles and the shape of a path of a centre shaft of the piston on circular arches the rotation support points being the centre point of the striking motions, and of positioning flow openings and grooves of medium,
Fig. 5 shows an application of a drive wheel belonging to a wheel pair of a power transmission device of a rotary piston engine according to the invention connected to a centre shaft of the rotary piston and of a second drive wheel connected to a main shaft and of alignment marks which are at the point of each other in the drive wheels in the situation of the figure,
Fig. 6 shows an application of a drive wheel belonging to a wheel pair of a power transmission device of a rotary piston engine according to the invention connected to a centre shaft of the rotary piston and of a second drive wheel connected to the main shaft, and
Fig. 7 shows cross-sections of an application of a rotary piston engine according to the invention, of a power transmission device with its drive wheels, a main shaft, a mounting support, bearings and a base. The figures show a piston 1, a wall frame 2 of a rotation space, a drive wheel 3 connected to the piston, a main shaft 4, a drive wheel 5 connected to the main shaft, a mounting support 6, a base 7, bearings 8, a cylinder block 9, covers 10, an inlet opening 11 of medium, flow grooves 12 of medium, an outlet opening 13 of medium, and outlet grooves 14 of medium. When moving the piston 1 in alternate strokes around its centre shaft K by rotating around a polar axis being in one of rotation support points P, PI, P2 or P3, a path of each piston angle is according to one of wall sections being in the wall frame 2 of rotation spaces shown in the figures and a section of a path of the centre shaft K of the piston is formed around the same rotation support point as the path of the piston angles. The rotation support points are eccentrically at a distance from a centre point of the rotation space of the piston such that an extreme end of a torque structure of the piston is at an extreme end of an eccentric structure of the piston at a distance of a relatively long, standard-length radius from the rotation support point of the striking motion. Between the wall frame 2 of the rotation space and the piston 1, there are two expanding and two contracting chambers.
In the strokes of the piston 1, the paths of piston angles and the section of the path of the centre shaft K of the moving piston are formed around a common rotation support point of circular-arch shape such that, on the centre shaft K of the piston, there is a planetary shaft rotating on a path of regular shape, which is the rotation axis of the piston.
Transmission of kinetic energy between the piston 1 and the main shaft 4 is arranged connectedly by a wheel pair, the drive wheel 3 belonging to it is connected at the point of the centre shaft K of the piston such that it moves according to the rotational motions of the piston moving on a path surrounding the centre point of the motion space of the piston rotating around rotation supports and at the same time spinning according to the spinning motions of the centre shaft of the piston, and the drive wheel 5 is connected to the main shaft 4 aligned to a centre point O of the motion space of the piston such that the drive wheels collecting the kinetic energy of two moment lines are within each other as a wheel pair and, by the gear ratio of the wheel pair, the rotational speed of the main shaft is about 1.72 times higher that the rotational speed of the piston.
Controls of the motions of the piston 1 are wall sections of the wall frame 2 of the rotation space along which the piston angles glide, bearings in the centre shaft and bearings in the main shaft 4. In the piston angles, there can be a roll and sealing material to decrease friction.
According to Figs. 1-3, the rotation cycle of the angles of the piston 1 is formed of twelve successive striking motion sections the polar axis being during one striking motion in one of three rotation support points P, PI or P2, which are at an equal distance from the centre point of the motion space. The extreme end of the torque structure of the moving piston 1 is at the extreme end of the eccentric structure of the piston at a distance of a relatively long, standard-length radius a from the support point P, PI or P2 of rotational motion such that the path of the piston angles is formed by three sections identical in relation to each other. The centre shaft K of the piston is always at a distance of a standard-length radius b from the same support point of rotational motion as the extreme end of the eccentric structure of the piston, and of sections A-B, B-C and C-A of the path of the centre shaft of the piston is formed a planetary path on the sections of which the angular speed of the centre shaft K of the rotating piston is constant. In Fig. 4, the inlet opening 11 of medium and filling chambers are designated with an open arrow and the outlet opening 13 and emptying chambers with a solid arrow. According to Fig. 4, the rotation cycle of the angles of the piston 1 is formed of sixteen successive striking motion sections the polar axis being in one of four rotation support points P, PI, P2 or P3, which are at an equal distance from the centre point O of the motion space such that the path includes four sections identical in relation to each other. When pressure or kinetic energy obtained from the main shaft 4 moves the piston 1, the path of the piston angles follows the wall sections of the wall frame 2 of the rotation space and each position of the piston controls pressure and underpressure via valve openings and grooves in the chambers of the rotation space such that the medium fills the chambers expanding of their volume and the chambers contracting of their volume are emptied. The extreme end of the torque structure of the moving piston 1 is at the extreme end of the eccentric structure of the piston, which is at a distance of a relatively long, standard-length radius a from the support point P, PI, P2 or P3 of rotational motion. The centre shaft K of the piston is always at a distance of a standard-length radius b from the same rotation support point as the extreme end of the eccentric structure of the piston, and of sections A-B, B-C, C-D and D-A of the path of the centre shaft K of the piston is formed a planetary path at a distance from the centre point O of the rotation space, on the sections of which the angular speed of the centre shaft K of the rotating piston is constant.
According to Figs. 5 and 6, the wheel pair 3, 5 of the power transmission device of the rotary piston engine is in connection with the piston such that the drive wheel 3 is connected at the point of the centre shaft K of the piston and the drive wheel 5 is connected to the main shaft 4 aligned to the centre point O of the motion space of the piston. The piston 1 moving in the motion space 2 spins around its centre shaft K and at the same time the centre shaft of the piston rotates around the centre point O of the motion space following a path k. The continuous contact of the drive wheels being within each other is arranged such that the difference between the length of reference diameters of the drive wheels is the length of the greatest diameter d of the path, and the length 2 x d of a reference diameter of the drive wheel is substantially two thirds of the length of a reference diameter h of the second drive wheel.
According to Fig. 7, the main shaft 4 of the rotary piston engine is aligned by the mounting support 6 to the centre point O of the motion space of the piston such that a wheel pair has been formed of the drive wheels 3, 5 and the cylinder block 9 and the mounting support 6 are mountedly on the base 7.
According to the application of Figs. 1-3, the figure system comprising a section limited by twelve 30-degree curved lines showing the cross-section of the path of the angles of the quadratic piston and the wall frame of the rotation space and a section showing three 30-degree sections on the circular-arch shaped path of the centre shaft of the piston is formed in the following way:
The points P, PI and P2 being the rotation support points of the striking motions of the piston are the vertex in an isosceles triangle the side length of which is the difference between the length of the hypotenuse and the length of the side of the quadratic piston. To mark the torque structure of the piston, the piston is illustrated with a lever arm a, the length of which is 0.7 parts of the length of the hypotenuse of the quadratic piston, and the outer end of which is at the extreme end of the torque structure of the piston the inner end being the polar axis in the rotation support point P, PI or P2. The distance of the centre shaft K of the piston to the rotation support point is a radius designated by a segment b the length of which is 0.2828 parts of the length of the piston side. As the previous striking section ends, the polar axis being at the inner end of the torque arm operating in the next stroke sets to its rotation support point. In the strokes around the rotation support points P, PI and P2, the piston angles are moved along the wall sections of the wall frame 2 of the rotation space and the centre shaft K of the piston is moved along the planetary path which includes bends A, B and C and sections A-B, B-C and C-A.
According to the application of Fig. 4, the figure system comprising a section limited by sixteen 22.5 -degree curved lines showing the cross-section of the path of the angles of the quadratic piston and the wall frame of the rotation space and a section showing four 22.5-degree sections on the circular-arch shaped path of the centre shaft of the piston is formed in the following way using coordinates:
In the strokes around the rotation support points P, PI, P2 and P3, the piston angles are moved along the wall sections of the wall frame 2 of the rotation space and the centre shaft K of the piston is moved along the planetary path, the bends A, B, C and D of which are at the point of the x axis and the y axis as the vertex in a quadratic figure, the length of the hypotenuse of which is 0.1718 parts of the length of the side of the quadratic piston and the centre point of which is at the point of the centre point O of the rotation space. The points P, PI, P2 and P3 being the rotation support points of the striking motions of the piston are the vertex in a square symmetrical in relation to the x axis and the y axis the length of the side of which is 0.33 parts of the length of the piston side. To mark the torque structure of the piston, the piston is illustrated with a lever arm a, the length of which is 0.7 parts of the length of the hypotenuse of the quadratic piston, and the outer end of the lever arm a is at the extreme end of the torque structure of the piston the inner end being the polar axis in the rotation support point P, PI, P2 or P3. The distance of the centre shaft K of the piston to the rotation support point is a radius designated by a segment b the length of which is 0.2828 parts of the length of the piston side. As the previous striking section ends, the polar axis being at the inner end of the torque arm operating in the next stroke sets to its rotation support point.
The drive wheel 3 provided with an inner cogged ring belonging to the power transmission device of the rotary piston engine according to the application of Figs. 5 and 6 is connected at the point of the centre shaft K of the piston such that it moves according to the rotational motions of the centre shaft of the moving piston by rotating and at the same time according to the spinning motions of the centre shaft of the piston by spinning. The drive wheel 5 cogged of its outer race is connected to the main shaft 4 aligned to the centre point O of the motion space of the piston such that the drive wheels are within each other. A reference diameter of the drive wheel 5 is substantially two times longer than the greatest diameter d of the path k of the centre shaft of the piston and two thirds of the length of a reference diameter h of the drive wheel 3, whereby the drive wheels 3 and 5 form a wheel pair which has simultaneously provided the transmission of kinetic energy between both the rotational motions of the centre shaft of the piston and the spinning motions of the centre shaft and the spinning motions of the main shaft such that for one piston round the main shaft spins for about 620 degrees.
Alignment marks L and M illustrate in Fig. 6 that the drive wheel 3 connected to the piston has rotated according to the alignment mark L starting from the situation of Fig. 5 for a 45-degree stroke spinning around the centre shaft such that the drive wheel 5 connected to the main shaft has rotated starting from the situation of Fig. 1 for about 77 degrees, as the alignment mark M shows.
The rotation support points of the rotary piston engine according to the invention implement the striking motions of the piston such that, on the path of the piston angles, there are at least three sections identical in relation to each other, and the even, continuous rotation of the centre shaft K of the piston is formed by a closed planetary path at the point of bends of which the rotations are gentle. The rotational speed of the centre shaft on the different sections of the planetary path is constant and each section equals the number of degrees of the striking section of the torque structure of the piston. The planetary path substantially includes as many bends as there are rotation support points. The striking motions of the piston and the sections of the paths of the centre shaft K of the piston are controlled in relation to each other in the rotation support points such that they have a common rotation support point, their striking sections are simultaneous and they include the same number of degrees.
The length of the lever arm a is the distance between the rotation support point and the extreme end of the torque structure of the piston, the angle being the extreme end of the torque structure is of the piston angles at the greatest distance from the rotation support point and the sections identical in relation to each other E-F, G-H and I-J of the path of the extreme end shown in Figs. 1-3, and the sections identical in relation to each other E-F, G-H, H-I and J-Kl of the path of the extreme end shown in Fig. 4 are the longest wall sections of the wall frame of the rotation space, and the angular speed of the piston angle moving at their point is constant when moving the piston at an even rotational speed.
According to the inventive idea, the 360-degree rotation of the angles of the moving piston is formed from at least twelve successive striking motion sections of circular- arch shape which are arranged to rotate for the duration of the striking motion around a polar axis being in one of at least three different rotation support points such that torque in the piston rotation around its centre shaft is even and to the path of the piston angles is formed at least three sections identical in relation to each other and the motions of the centre shaft K of the piston are on a planetary path which includes substantially the same number of sections and bends, at the point of which rotations are gentle, for the rotation support points such that inertia forces caused by the motions of the piston are controlled. Bends on the path of the centre shaft and the path of the piston angles are the gentler, the more there are rotation support points and, between the piston and the main shaft of the rotary piston engine, there are two moment lines available for transmitting kinetic energy, which are arranged connectedly from both the rotational motions of the piston around the rotation support points and the spinning motion of the piston around its centre shaft.
When the piston 1 is moved by the pressure effect of a medium, e.g. vapour, or by kinetic energy obtained from the main shaft 4, the medium is conveyed to chambers expanding of their volume of the rotation space of the piston through the inlet opening and grooves shown in Fig. 4. Due to a groove, an opening is formed in the wall of the rotation space from which the medium flows around the corner. From the chambers contracting of their volume, the medium exits through the outlet opening and grooves shown in Fig. 4. It is natural that, in the different applications of the invention, the rotational motions and rotation of the piston can be switched to the right or the left or into both directions, e.g. the size and shape of the openings and grooves can be different from the application of Fig. 4 and e.g. the piston walls can include recesses and projections of different shapes.
Within the scope of the invention, it is possible to consider arrangements differing from the above within the scope of the inventive idea defined by the claims e.g. by varying by computer software. Therefore, the rotation space of the piston of the rotary piston engine can be formed for a triangular or e.g. hexagonal rotary piston.
According to an application of the invention, the drive wheel belonging to the power transmission device of the rotary piston engine is connected to a crank device mounted as an extension of the centre shaft of the piston such that it moves rotating according to the rotational motions of the piston and at the same time spinning according to the spinning motions of the centre shaft of the piston, and the second drive wheel belonging to the power transmission device is connected to the main shaft aligned to the centre of the motion space of the piston such that the drive wheels form a wheel pair connecting the crank device and the main shaft. According to an application of the invention, the power transmission between the piston and the main shaft of the rotary piston engine is arranged by an intermediate shaft which is not parallel with the centre shaft of the piston and which is between the piston and the main shaft pivotedly mounted from its both ends.
According to an application of the invention, operating pressure of the rotary piston engine is arranged produceable in the motion space of the piston.
The invention is not limited to the advantageous embodiments described but it can vary within the scope of the inventive idea defined by the claims.

Claims

1. A rotary piston engine, which includes: a piston (1), a motion space of the piston, in which striking motions of the piston (1) are arranged to rotate such that a rotation support shaft is in one of stationary rotation support points being at an equal distance from a centre point of the motion space, and for a path of a centre shaft of the piston is formed a planetary path such that, at the point of the centre shaft of the piston (1) or in its immediate vicinity, there is a planetary shaft being the rotation axis of the rotation of the piston (1), and - a power transmission device, characterised in that the 360-degree rotation of angles of the moving piston (1) is formed from at least twelve successive striking motion sections which are arranged to rotate for the duration of the striking motion around a polar axis being in one of at least three different rotation support points (P, PI or P2) such that torque in the piston rotation around its centre shaft (K) is even and to a path of the piston angles are formed at least three sections identical in relation to each other and motions of a centre shaft (K) of the piston are on a planetary path which includes substantially the same number of sections (A-B, B-C, C-A) and bends (A, B, C), at the point of which rotations are gentle, such that inertia forces caused by the motions of the piston are controlled, and that of rotational motions of the piston around the rotation support points (P, PI or V2) and spinning motions around its centre shaft (K) are arranged two connectable moment lines between the piston (1) and the main shaft (4) suitable for transmitting kinetic energy.
2. A rotary piston engine according to claim 1, characterised in that the number of rotation support points of the piston is dividable by three and that walls of the motion space of the piston are formed by three sections identical in relation to each other.
3. A rotary piston engine according to claim 1, characterised in that an extreme end of a torque structure of the moving piston (1) is at the distance of a relatively long, standard-length radius (a) from a rotation support point (P, PI or P2) of a striking motion.
4. A rotary piston engine according to claim 1, characterised in that sections of a wall frame (2) of the rotation space of the piston are of circular-arch shape.
5. A rotary piston engine according to claim 1, characterised in that angular speed of the extreme end of the torque structure of the moving piston (1) is constant.
6. A rotary piston engine according to claim 1, characterised in that the centre shaft (K) of the piston is at a distance of a standard-length radius (b) from the rotation support point (P, P2 or P2) of the striking motion.
7. A rotary piston engine according to claim 1, characterised in that sections (A- B, B-C, C-A) of a planetary path of the centre shaft (K) of the piston are of circular-arch shape.
8. A rotary piston engine according to claim 1, characterised in that between the piston (1) and the main shaft (4) is arranged power transmission comprising two moment lines with drive wheels (3, 5) by connecting a drive wheel (3) to the piston substantially at the point of the rotation axis (K) of the piston and by connecting a second drive wheel (5) to the main shaft (4) aligned substantially to the centre point (O) of the motion space of the piston such that the drive wheels (3, 5) form a wheel pair.
9. A rotary piston engine according to claim 1, characterised in that, in power transmission, a reference radius of one drive wheel (3 or 5) is substantially the length of the greatest diameter (d) of the path (k) of the centre shaft of the piston.
10. A rotary piston engine according to claim 1, characterised in that, in power transmission, the length (2 x d) of a reference diameter of one drive wheel (3 or 5) of the wheel pair is substantially two thirds of the length of a reference diameter (h) of the other drive wheel.
EP12817318.4A 2011-07-26 2012-07-18 Rotary piston engine Withdrawn EP2737177A4 (en)

Applications Claiming Priority (2)

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FI20115769A FI125503B (en) 2011-07-26 2011-07-26 Rotary piston engine
PCT/FI2012/050740 WO2013014335A1 (en) 2011-07-26 2012-07-18 Rotary piston engine

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FI124756B (en) * 2013-12-12 2015-01-15 Steammotor Finland Oy Ab Ltd Rotary piston inserter

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US3097632A (en) * 1959-04-17 1963-07-16 Nsu Motorenwerke Ag Rotary internal combustion engine and method of operation thereof
US3226013A (en) * 1964-05-04 1965-12-28 Toyota Motor Co Ltd Rotary machine
US3359954A (en) * 1966-04-05 1967-12-26 Nsu Motorenwerke Ag Rotary internal combustion engine and method of operation thereof
GB1533050A (en) * 1976-07-02 1978-11-22 Whitestone B Rotary fluid-machine
FI101411B1 (en) * 1996-09-03 1998-06-15 Risto Antero Auvinen Power transmission device for rotary piston motor
FI20085817L (en) * 2008-09-02 2010-03-03 Steammotor Finland Oy Ab Ltd Planetary rotary piston engine

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FI20115769A0 (en) 2011-07-26
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FI20115769A (en) 2013-01-27
WO2013014335A1 (en) 2013-01-31

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